Apparatus for freezing ice



Jan. 31, 1939.

C;A Mul-FLY 2,145,774

APPARATUS FOR FREEZING ICE Filed April 5, 1934 6 Sheets-Sheet l Jan. 31, 1939. G. MUFFLY 2,145,774

APPARATUS FOR FREEZING ICE Filed April 5, 1934 6 Sheets-Sheet 2 INVENToR. Gle/7 77 Ma( f'ly. E 4

A TTORNEYS.

Jan. 31, 1939. G, Mul-FLY 2,145,774

APPARATUS FOR FREEZING ICE Filed April 5, 1934 6 Sheets-Sheet 3 INVENTOR. @Zar/27 /Wafffry A TTORNEYS.

Jan. 31, 1939. G, Mur-'FLY 2,145,774

APPARATUS FOR FREEZING ICE Filed April 5, 1934 6 Sheets-Sheet 4 VIL# INVENTOR. G7627?? Mln/fig,

Jan. 31, 1939. c; MUFFLY 2,1459774 APPARATUS FOR FREEZING ICE Filed April 5, 1934 6 Sheets-Sheet 5 jfl-5' 35i 532 33d INVENTOR. Glen/7 /V/z ff Zig.

A TTOFNEYS.

Jan. 31, 1939. G. MUFFLY 2,145,774

' APPARATUS FOR FREEZING ICE Filed April 5, 1934 6 Sheets-Sheet 6 EEES NVENTOR. 6767777 /V/'z/ff/g,

BY Z @Lw/lm /W ATTORNEYS.

Patented `lan. 31, 1939 UNITED STATES PATENT OFFICE 52 Claims.

This invention relates to refrigerating mechanism and particularly to such mechanism as is applicable to the production of ice as well as to the provision of a new and novel method of producing ice and controlling the operation of the mechanism during such production. It is an improvement on the construction shown and described in my co-pending application for Letters Patent of the United States for improvements in Refrigerator and method and apparatus for freezing ice, filed November 8, 1933, Serial No. 697,124.

Objects of the invention include the provision of improved valve mechanism for controlling the flow of refrigerant; the provision of a valve mechanism for controlling the flow of refrigerant in which the pressure of the liquid refrigerant is employed to actuate the valve; the provision of a method and apparatus for freezing ice by means of refrigerating mechanism so constructed and arranged as to provide an operating cycle which employs specific heat of the liquid refrigerant to melt ice free from the evaporating surfaces, yet does not dump liquid refrigerant into the suction :5 passage of the mechanism.

Another object is the provision of a refrigerating mechanism for freezing water to produce ice including more than two sets of ice-making surfaces connected in multiple circuits with the l refrigerating mechanism and so constructed and arranged that one set only will be active in the production of ice, thus allowing more time for melting ice free from the surfaces of the other sets upon which it has been frozen.

,; Another object is to provide a two-way expansion valve, that is, one in which the flow of liquid refrigerant through the valve may be reversed without otherwise affecting the operation of the valve.

Another object is to provide a refrigerant flow control device so constructed and arranged as to produce a delayed action in the operation of certain of the valves thereof; and the provision of a refrigerant flow control mechanism including a fluid charged bellows for actuating said control element and in which expansion or contraction of the bellows is effected both by temperature changes affecting the fluid with which it is charged and by the changes in pressure surrounding the'bellows.

Other objects are to provide, for use in a refrigerating mechanism, a one-way pressure regulating device which acts as a check valve, allowing free flow of refrigerant in the opposite direction; to provide in a refrigerant circuit means for controlling the flow of refrigerant therein including means acting to restrict the flow of refrigerant in one direction and to serve as a float opening valve when the refrigerant is flowing in the opposite direction; and to provide a means for controlling the flow of refrigerant in a refrigerating mechanism including a restricting device having a capillary passage therethrough and so constructed and arranged as to periodically free itself of obstruction by flushing it with liquid refrigerant and opening of the restricting passage.

Another object is to provide an improved form of evaporating element for use in connection with a freezing surface and in which the refrigerant flow is so controlled as to prevent a delayed refrigerating effect.

Another object is to provide a valve mechanism for a refrigerant circuit in which the warm and cold portions of the valve mechanism are separated by thermal insulation and by location so that the specific heat of the liquid refrigerant may be utilized for the purpose of melting ice free from an evaporating surface.

Another object is the provision of a refrigerant control device including a thermal element and so constructed and arranged that the thermal element ls not required to furnish power for actuating certain other elements but only to control the application of power provided for effecting the movementv of such other elements.

Another object is to provide means for freezing water to provide ice including a freezing surface and an evaporator element and in which provision is made for flexibility between the freezing surface and the evaporator elements whereby to insure better thermal contact therebetween.

Another obi ect is to provide refrigerating means for producing ice including a freezing surface and a control means for the flow of refrigerant therethrough and in which the control means is actuated in response to a temperature rise occurring only upon the freeing of ice from the surface upon which it has been frozen.

A further object is to provide an evaporator structure capable of withstanding relatively high internal pressure yet made of relatively light gauge metal so that a minimum amount of heat is conducted through the metal in the direction of the plane thereof.

Still further objects are the provision of certain methods of operation and of control of apparatus for refrigerating mechanism particularly applicable to such apparatus employed in the artificial production of ice.

The above being among the objects of the pres- Cil ent invention, the same consists in certain novel features of construction, combinations of parts, and methods of control and operation, to be hereinafter described With vreference to the accompanying drawings, and then claimed, having the above and other objec's in View.

In the accompanying drawings which illustrate suitable embodiments of the present invention and in which like numerals refer to like parts throughout the several different views,

Fig. 1 is a more or less diagrammatic, broken, partially sectioned view of a refrigerating apparatus embodying an improved refrigerant flow controlling apparatus, the valve mechanism of which is shown in section and enlarged with respect to the remaining elements.

Fig. 2 is an enlarged, partially broken, partially sectioned side elevational view of the dual expansion valve illustrated in Fig. 1.

Fig. 3 is a view similar to Fig. 1 but illustrating a constructon in which more than two sets of ice making evaporators are employed together with a modified form of valve mechanism for controlling the refrigerant circuit for the evaporator.

Fig. 4 is an enlarged, partially broken, partially sectioned side elevational View of the valve member for one of the three restricted check valves shown in Fig. 3.

Fig. 5 is an enlarged vertical sectional view taken centrally through one of the thermal. elements employed in connection with the suction tube of the construction shown in Fig. 3, and taken on the line 5-'5 of Fig. 3.

Fig. 6 is a partially broken, vertical sectional view taken centrally through a modified form of valve mechanism of the type disclosed by Fig. 1.

Fig. 7 is a fragmentary, partially broken, vertical sectional view of a modification for part of the mechanism shown in Fig. 6.

Fig. 8 is a perspective view of the saddle for the spring employed in the'construction showin in Fig. 7.

Fig. 9 is a fragmentary vertical sectional view illustrating in greater detail' a portion of the mechanism shown in Fig. 6.

Fig. 10 is a chart or graph illustrating the approximate temperature and pressure conditions that may affect the bellows in the construction shown in Fig. 6.

Figs. 1l to 18, inclusive, are enlarged vertical sectional views of Various modified forms of the restricting check valve illustrated in Figs. 3 and 4 in particular.

Figs. 19, 21, 22, 24 and 26 are fragmentary vertical sectional views taken through modified forms of ice-making cups or cones and their evaporating units such as are diagrammatically illustrated at 3i in Figs. 1, 3 and29.

Fig. 2O is a horizontal sectional view taken through a modification of the construction show in Fig. 19.

Fig. 23 is a fragmentary vertical sectional view taken on theline 23-23 of Fig. 22.

Fig. 25 is a fragmentary 4horizontal sectional View taken on the 1in@ 25-25 of Fig. 24.

Fig. 27 is a vertical sectional view taken axially through a plurality of ice cones such as those fr; zen on the evaporating surfaces illustrated on the same sheet therewith and particularly in Fig. 2S, illustrating the manner in which they will nest together in storage and in use.

Fig. 28 is a sectional and diagrammatic view of a refrigerating system combining several of "re features disclosed in the previous views and including further modifications and/or refinements.

Fig. 29 is a reduced diagrammatic view showing the path of refrigerant through the various evaporator units and the capillary tube of Fig. 28.

Fig. 30 is a horizontal sectional view taken through one of the evaporator units of Fig. 28 as on the line 30-30 of Fig. 28.

Fig. 31 is a fragmentary sectional view taken on the line 3i-3i of Fig. 28.

It will be readily understood by those skilled in the art that certain of the methods and apparatus herein disclosed are applicable for uses other than the production of ice but, in view of the fact that the present application deals principally with the artificial production of ice, the

description and explanation herein, primarily for the purpose of illustration, will be limited entirely to the application of such methods and/or apparatus to their use in the artificial production of ice.

In my previous application above identified means are disclosed for the production of ice by artificial refrigeration and includes, in certain of the modications there shown, a refrigerating mechanism including a compressor, condenser and receiver constituting a refrigerant high side, a water tank the bottom of which has associated therewith certain surfaces which, for the simplicity of explanation, will be referred to as cups or cones, exposed tov the water within the tank, and each of which has associated with its unwetted surface an evaporating element or refrigerant low side for the purpose of refrigerating it. Preferably. the cups or cones are connected in series or in parallel, or as herein described may be connected in series, in parallel, or a combination of both with the compressor and condenser. Suitable control means are provided in the connection between the high and low sides and between certain series or groups of the cups or cones so that one set or group of cups or cones will be refrigerated so as to cause ice to be formed in or on the same, while the other group of cups or cones will be warmed in order to cause ice 5 through the two sets or groups of cups or cones' so as to effect a constant and continuous production of ice.

The present invention deals primarily with the same type of construction as disclosed in said co-pending application above identified but relates to certain improvements therein. Accordingly, there is illustrated in Fig. 1 a refrigerating mechanism including a high side indicated generallyat I0, a low side indicated generally at I2 and a control mechanism indicated generally at I I. The highside includes the usual motor driven compressor 12. condenser 13 and receiver 14. The low side includes two groups of evaporating units in the form of rings 3| connected in series through the dual expansion valve 36, each series being subdivided into two smaller groups the individual rings of which are connected in parallel. Each ring 3| of the groups 21 and 28 of rings 3| is thermally associated with a corresponding ice making surface arranged in a water tank 9, the groups 2l and 28 preferably being arranged at opposite ends of the tank 9 or otherwise spaced apart to minimize heat transfer between them. The control unit I| includes suitable valves for controlling the direction of flow of refrigerant from the high side I to the low side I2 together with thermal responsive means inthe form of bellows 63 and 64, the entire control unit being such that the direction of flow of refrigerant through the low side |2 may be periodically reversed.

Any refrigerant may be employed in connection with this refrigerating system, but it is preferable to use one having a high ratio of specific heat of liquid to latent heat of vaporization, such as dichlorodiiluoromethane, for instance, so that ample heat is available for melting the ice free from the refrigerated surfaces.

It will also be understood that any desired and/or conventional form of control means may be employed in connection with the refrigerating system as a whole for effecting cyclic operation of the system, where such cyclic operation of the system is desired.

The valve assembly is connected with the evaporator assembly I2 by means of two tubes I3 and I4, which act alternately as liquid and vapor passages. Liquid refrigerant is introduced through tube I5 to the tubes |6 and I1, but in the position of valves as shown it must flow through tube I6 and port I8, since port I9 is closed by valve 2| while valve 20, controlling port |8 is lifted from its seat by guide 22 of piston 24. It will be noted that the corresponding guide 23 of piston 24 has receded from the valve 2 I, allowing it to close under the action of spring 25, while spring 28 of valve 2|) is compressed.

After passing through the port I8 the liquid refrigerant, which is still warm and under high pressure, passes through tube I4 to the right hand section 28 of evaporator I2, where it first enters the tubular passage 30, connected in manifold to the evaporator rings 3| of section 28, thence the warm liquid passes through the various evaporator rings 3|, but it does not evaporate on account of the fact that it is still under high pressure. The warm liquid serves to heat these rings 3| in section 28 of the evaporator, and then passes through tubes 32 and 34 to the expansion valve 36, which is of a dual type as shown in more detail in Fig. 2.

Continuing to trace the refrigerant flow through the expansion valve in Fig. 2, it will be noted that the liquid refrigerant enters the chamber 31, surrounding the bellows 39, which bellows is compressed by the high pressure of the refrigerant so that the valve 4| is closed by the spring 43. The liquid therefor passes through port 46 to chamber 38. 'Ihe port 46 is opened by valve 42 during this period of operation because the bellows 40 is surrounded by low pressure 'refrigerant and the bellows expands under action of an internal spring similar to spring 41 in bellows 39, compressing spring 44 and lifting valve 42 from its seat. The action of bellows 4U, spring 44 and valve 42 are the same as in an ordinary expansion valve, so need not be described here in detail. Bellows 39, spring 43 and valve 4| are in effect inoperative at this time, since the bellows is compressed and the valve remains closed, so the action is the same if an ordinary expansion valve were used with provision for flow in a single direction. It may be noted in passing, however, that it is preferable to employ a small tube such as 52 to connect and thereby equalize the pressure in the interior of the bellows 38 and 40.

The refrigerant, which is now at low pressure, leaves chamber 38 through tube 35 and continuance of its flow may be traced in Fig. 1. Passing through tube 35 and tubes 33 the low pressure refrigerant now enters evaporator rings 3| in section 21 of the evaporator I2, where it evaporates, picking up heat from the walls of the rings 3| in such section. It will be understood that the heat comes from water in a tank having areas in Contact with these evaporator rings 3|, as shown in Fig. 28, for Instance, thus causing the water to freeze in the tank adjacent to the evaporator rings.

The vaporized refrigerant then passes through tubes 29 and I3 to the valve assembly II, where it is free to pass the guide 23 of piston 24 on account of this guide being provided with longitudinal flutes 54, and it then passes through cylinder bore 55, from which the piston 24 is slightly withdrawn, into chamber 6| surrounding bellows 63, thence partially through port 65 of wall 66 in housing 61 and out through passage 68 and tube 69 through an additional evaporator 10 to suction tube 1|. The vaporized refrigerant is then compressed by compressor 12, condensed in condenser 13, collected as liquid in receiver 14 and returned as warm liquid under high pressure through tube leading to tube |5, where it repeats the circuit as described.

This operation continues until the desired thickness of ice is formed on the wall surfaces of the water tank adjacent to the evaporator rings 3| of evaporator `section 21. With the reduction of heat transfer rate resulting from such formation of ice the refrigerant temperature in tube I3 and chamber 6| drops, cooling the bellows 63 and the volatile fluid 16 contained therein, reducing its vapor pressure within the bellows until the bellows 63 contracts under the action of the higher vapor pressure of fluid 16 in the warmer bellows 64. The bellows 64 is warmer because it is not directly in the path of the cold refrigerant, being contained in a substantially dead vapor body in chamber 62. As the internal pressure in bellows 64 overcomes the pressure in bellows 63 the rod 19 moves to the left, compressing bellows 63.

The springs 11 and 'I8 in these two bellows may be omitted, but are shown as a means of obtaining adjustment. By removing the plugs covering the screws 80 and 8| they may be adjusted inwardly to push the bellows heads 82 and 83 closer together thereby putting more compression on springs 11 and 18; adjusted outward to reduce such compression; or one screw adjusted inward and one outward to shift the normal position of rod 19 and the bellows heads 84 and 85 to which rod 19 is attached. In this manner the action of the two bellows may be balanced, cycles shortened or prolonged, etc., as will be understood from the following description of how the bellows act to control the operation of valves.

Returning now to the description of the bellows operation due to the cooling of bellows 63 while bellows 64 remains at a constant temperature or is warmed by its isolation from the cold refrigerant and its proximity to the warm liquid. it will be understood that the bellows head 85 and bellows head 84 are both moved to the left and that head 34 will move the arm 86 clockwise about its pivot |08, pulling the toggle link 88 downward and the stop 90 away from the wall 66, and stretching the spring 92. The result of this movement is to move the pin |02 and the toggle link 96 downward until the center of I 02 is below the straight line between pin and pin 98. 'I'he toggle formed by links 88 and 96 has been in locked position, where it was held by spring 92, which in this position has a considerable leverage over the corresponding spring 93 on the other side. However, as soon as the right hand toggle moves out of its locked position the piston 24 is moved to the left by the high pressure liquid in passage |04.

As soon as this liquid pressure has unseated valve 58 from seat 60 the high pressure liquid acts upon the full area of piston 24 in cylinder 56, carrying the piston and the two toggle mechanisms past the poin't where spring 93 obtains an increasing leverage advantage over spring 92. Meanwhile the movement of piston 24 to the left has allowed valve 20 to seat, closing its port I8 and stopping the ow of liquid through tube I6. Simultaneously the left end of piston 24 has entered cylinder 55 where it encounters only. low pressure vapor. The piston is guided into its cylinder by the iiuted guide 23, which fits freely in passage of the valve body |01. At the final movement of piston 24 to the left, when the spring 93 is in position to exert a forcible thrust on piston 24 through the toggle links 89 and 91 and the pin 99, the guide 23 strikes the stem of valve 2|, causing this valve to open against the pressure of liquid refrigerant in tube I1. The left hand toggle then locks itself with pin |03 justover center and stop 9| in contact with wall 66.

This movement of the parts leaves valve 20 closed, valve 58 and cylinder 56 open,'valve 51' closed, and valve 2| open. The refrigerant flow is thus reversed in the part of the system affected, so that liquid ows through tubes I1, I3 and 29 to the evaporator units or rings 3| of section 21. thence through passages 33 and 35 to thel expansion valve 36. From the expansion valve the low pressure refrigerant flows through passages 34 and 32 to the evaporator units or rings 3| in section 28, where a considerable part of it evaporates, and it then flows through passages 30 and I4 to passage |04 and out through cylinder 56 into chamber 62, where it acts to cool bellows 64 and prepare for another reversalof operation.

At the time that piston 24 is Withdrawn from cylinder 56 in the movement thus described, it will be seen that the liquid contained in evaporator section 28 is released to flow into chamber 62 and thence through passage 68 to the second evaporator 10, which is thus fed periodically with liquid refrigerant in addition to that which reaches it more slowly during the balance of the cycle. The evaporator is accordingly designed to accommodate such fluctuations in its liquid refrigerant content by providing it with ample internal volume.

While liquid is passing from the comparatively warm evaporator section 28 to chamber 62 there is a sudden increase of pressure in both chambers 6| and 62, which would cause both bellows to contract if it were not for the facts that they are tied together by the rod 19 and that each contains a rather still spring, 11 in 63 and 18 ln 64. The warm liquid will at first tend to expand bellows 64, which does no harm, but care must be used in the design of the case 61 to insure against liquid trapping around the bellows, as it would then boil off slowly and refrigerate the bellows to a point that might cause a premature reversal of the valves. It should be remembered that pressure alone (within the working range) will not compress either bellows because they are tied together, hence the analysis of bellows action is based on temperature, and while the liquid is momentarily raising the pressure in chambers 6I and 62 it is also raising the temperature to something above that of the bellows 63 at the time its contraction causes the mechanism to trip and reverse the valves.

Referring again to Fig. 2 and tracing the action of the reversible expansion valve 36, we nd that after the valve reversal as described the liquid refrigerant entered the chamber 38 through passage 35. This will cause bellows 40 to contract under pressure, which contraction is stopped before it damages the bellows by means of a sleeve similar to |08 in bellows 39. 'Ihis sleeve acts as a guide to keep the bellows in line with the valve, as a stop against undue compression in bellows length, and as a stop against damage to convolutions due to pressure exerted on side walls externally.

The valve bodies |06 and I 01 are attached to the housing 61 by means of studs or screws (not shown) and are made gas-tight by means of suitable gasket rings which are shown. These gaskets also serve to break the metallic conductivity of heat so that very little of the heat of the warm liquid refrigerant will be lost by conductivity to the cold body 61. It will also be found advisable to insulate the tubes I3, I4, I5, I6 and I 1 as well as valve bodies |06 and |01 from cold air as indicated by broken line in the event that these parts are located in a refrigerated space.

Parts 24 and 19 are free fits in holes through wall 66, they are guided in these holes and the wall restricts but does not entirely prevent refrigerant flow from one side to the other. The housing 61 is made gas tight with a suitable cover and gasket. Tapped lugs are shown for securing such a cover or covers.

Parts 86 to 91 inclusive and |00 to |03 inclusive may be duplicated, one set on either side of piston 24, as indicated by part 89 which is broken to show two similar parts of the same number. Pins 98 and 99 would each pivot two side members to the piston 24 in'that event.

In Fig. 3 is shown a mechanism somewhat similar to that shown in Fig. l, but arranged to produce cycles of alternate freezing and melting in three evaporator sections instead of in only two. In this case the valve mechanism is shown as operating to refrigerate one section while two are heated with warm liquid refrigerant. It will be understood that similar means may be employed to refrigerate two while one is heated, or to operate more than three sections with any desired number refrigerated while the balance are heated.

In Fig. 3, as in Fig. 1, the evaporator is shown diagrammatically in reduced scale as compared with the valve mechanism. Also it will be understood that the features of thermal break, insulation, etc. of Fi-g. 1 will apply to Fig. 3 although not repeated in this View. The representation of condensing means and the second evaporator in Fig. 1 are also understood to apply equally to Fig. 3 for the purpose of considering the operation of the complete system.

In Fig. 3 the high pressure liquid from condensing unit of the refrigerating system enters at port |5,-which is equivalent to tube I5 in Fig. 1. Liquid is carried thence through passage ||6 to the three valve chambers |I1, ||1 and ||1", but in the position shown the port leading from the latter is closed by valve IIB", while valves ||8 and H8 are unseated, allowing liquid to pass. These three valves are constantly urged toward `their seats by springs ||3 and are periodically unseated, as will be described, by guides |20, and |20, each of which is provided with flutes |2| to allow refrigerant to pass.

The liquid, after passing valves ||8 and H8' enters tubes |22 and |22' leading to evaporator the ice that has previously been frozen in the water associated with these elements as previously referred to in the description of Fig. 1. After passing through the elements of evaporator sections |23 and |23 the liquid refrigerant, still under high pressure, iiows upwardly, lifting the check valves |24 and |24', and iiows to the right in passage |25 until it is checked by valve |24. These three check valves, referred to generally as |24, are slightly heavier than the liquid refrigerant used in the system, hence |24 rests upon its seat |26, and is aided in seating by the pressure of the liquid refrigerant, and checks the downward flow of refrigerant at this point, whereas |24 and |24 are lifted from their seats |26 and |26 by the upward flow of liquid. Each of the three check valves is, however, provided with an internal passage as shown partially in section in Fig. 4, so that refrigerant may flow through the body of the valve itself in a downward direction, even when the valve is seated, but under a restriction which reduces the pressure of the refrigerant to something below its boiling point. Under suchconditions the seated valve |24 serves the same purpose as an expansion valve. Several variations of such valves are shown in more detail in Figs. 11 to 18 inclusive and will be described in detail later. The entry port |21 and the exit port |28 for the valve |24 shown in Fig. 4, are connected by a capillary or other restricting means which may be of any one of the types disclosed in connection with Figs. 11 to 18 inclusive for the purpose of controlling the rate of refrigerant flow in the downward direction, while upward fiow is substantially unrestricted.

The refrigerant, at reduced pressure, now flows through evaporator elements 3| of section |23", where it evaporates, picking up heat from the water contained in the tank (not shown but previously referred to) arranged to contact the evaporator rings 3|. The vaporized refrigerant then flows through tube |22, chamber |29", flutes |2| of guide |20, past Valve seat |30 from which valve 3| is shown lifted, through cylinder |32" from which piston |33" is withdrawn, and into chamber |34 of casing |35, from whichlit is withdrawn by suctioncf the compressor through passage 68, which corresponds to passage of the same number in Fig. 1.

This completes the circuit of refrigerant during that portion of the cycle when the valves are positioned as shown in Fig. 3. The solid arrows indicate path of high pressure refrigerant and the dotted arrows indicate path of low pressure refrigerant during this period.

It will be noted that each of the tubes |22, |22 and |22 pass through a housing |36, |36 or |36, respectively, of which |36 is shown in section. Fig. 5, taken on the lines 5-5 of Fig. 3 shows another section of this housing, which i's the same in each of the three cases.

Referring to Fig. 5, the housing |36 is shown to comprise a chamber |31, containing a liquid |33 which freezes within the operating range of the system and expands upon freezing, a diaphragm |39, and a second chamber |40, containing a non-freezing liquid |4I. In Fig. 5 the tube |22 is considered to equally represent tubes |22 and |22" as well, since the action is the same for each at its respective period of the cycle.

At the positions of values shown in Fig. 3 the tube |22" is refrigerated and this tube (|22 in Fig. 5) cools the freezing solution |38 in chamber |31, which is entirely filled by it. The first freezing will occur around the tube, so that ice forms in the bottom of chamber |31 first and as the freezing continues upward the diaphragm |33 is pushed upward, causing some of the nonfreezing solution 4| in chamber |40 to ow out into tube |42" (Fig. 3) under a high pressure.

Referring again to Fig. 3, it will be seen that when tube |22 has been refrigerated for a period long enough to freeze the desired thickness of ice adjacent to evaporator elements 3| of section |23 and the temperature of |22" is further reduced by the retarded heat transfer rate thus brought about in section |23", the solution |38 in casing |36" will have frozen enough to cause the diaphragm |39 to push some of the nonfreezing liquid |4| out of chamber |40 into tube |42", increasing the pressure of liquid |4| in housing |43, thus causing the iiexible metal bellows |44 to compress and push the rod |45 upward.

The rod |45 in moving upwardly strikes arm |46.of toggle link and moves the pin |5| to the left until it is beyond the center line between the pins |52 and |53, in which position the liquid pressure, acting upon piston |33, pushes it away from valve seat |30 and out of its cylinder bore, so that the pin |5| is moved farther to the left to engage the left end of slot |51 in the pull rod |58. At the same time the pin |52 moves the arm |53 of the bell crank |60 upwardly and the bell crank moves the push rod 6| to the right, pushing pin |5| toward the center line between pins |52 and |53". Toggle link |54" is then pulled farther to the right by spring |62" until it goes over center and locks piston |33" down against the valve seat |30".

The upward movement of the piston guide |20 releases liquid valve |8 which is closed by its spring H9, while the downward movement of piston |33" and its guide |20" opens valve H8" against its spring ||9. The total result is that the refrigerant circuit is thus changed to follow a new path as follows:

Warm liquid at high pressure passes valves I8 and ||8" to tubes |22 and |22", heats evaporator sections |23' and |23, passes valves |24 and |24", is reduced in pressure by valve |24, evaporates in section |23, returns as vapor through tube 22, passes valve seat |30 into chamber |34 and goes through passage 68 to the condensing unit. This causes ice to freeze adjacent to evaporator section |23 while section |23 is heated to melt ice free which has previously formed on its associated tank surface. The tube |22, now being cold, causes liquid |38 to freeze in chamber |31 of housing |36, while the tube |22, being warm, causes ice in housing |36" to melt and bellows |44 to reexpand so that rod |45 drops down out of the way for the next movement, which will bring arm |46 down again, locking toggle links |50 and |54 as before.

When water has been frozen to ice at group m and 1n chamber m. the bellows m' wm push the rod |45' upward, moving rod |41 and rocker |48 until pin |8|' goes over center to the right and piston |33 is released to move under the pressure of the liquid refrigerant. Pin ill' and pull rod |88 pull pin ill back nearly to center v and spring |82 relocks toggle formed by links |88 and |84.

When water has been frozen to ice at group A |23' and in chamber |38'. the ebellows |44" is compressed, pushing rod |45" upward and the mechanism snaps back to the position shown in the drawings, lthe movement of pin |8i" to the v left moving rod |83 to theV left and locking the middle toggle mechanism.

'I'he cycle of operation provided by the valve control mechanism and evaporator arrangement shown in Fig. 3 provides one method of prolonging the period for melting ice free from the surface upon which it has been frozen. This maybe desired in some cases where the system is charged Y with a refrigerant having a low specific heat of invention contemplates designs adapted to a wide variety of conditions with any required ratio of freezing to melting time.

-For certain of these conditions it is possible to use a much simpler type of valve mechanism, employing a single bellows or diaphragm foi the multiple purpose of eifecting various steps in a series of valve actions. It is possible to make one bellows perform various required functions by alternately causing it to contract with reduction of temperature and expand with reduction of surrounding pressure. An example of a mech- -anism accomplishing this result is shown in Fig. 6 which will now be referred to.

Fig. 6 may be considered as replacing assembly of Fig. 1, with connections as numbered leading to the same evaporator and condensing devices, though the secondary evaporator 10 is not required when the valve mechanism of Fig.6 is employed. The reason for this is that Fig. 6 provides means for evaporating all of the refrigerant in the ice-maker evaporator without dumping any of the liquid into suction line 88.

With the valve positions as shown in Fig. 6 the refrigerant enters from tube |1 (Fig. l) Aand follows the solid arrows through valve port i8, the valve 2| being lifted by piston 24 at its extreme travel to the left, and from there the liquid flows through tube i3 (Fig. 1) to the left hand evaporator section 21. It is reduced in pressure by the dual expansion valve 38, evaporated in group 28 of the evaporator rings 3| and returns through tube I4 to the open vapor valve |84 at the upper right of Fig. 6, and through chamber |1| to the outlet port 88 leading to tube 88 or 1| of Fig. 1.

The freezing operation is the same as described in connection with Fig. 1, but as shown by Fig. 6 the housing |10 is open to allow the vapor to flow through the entire chamber |1| and over the one bellows |12 at all times. This bellows is urged to expand by the spring |13 and the vapor pressure of volatile fluid |14 with which it is charged.

The arrangement in Fig. 1 will insure rt wm be understood that a. more volatile uuid |14 .would require that the spring |13 be under' atl |18. This causes contact point |80, which is integral with rocker |18 to; depress the plunger 15 |8| against the action ofthe spring |82, disengaging the plunger from the notch |83 in piston 24', which has been thereby held at its extreme leftward position.

The piston 24', upon being so released, moves to the right under the force exerted upon its left end by the high pressure liquid refrigerant. I'his movement of the piston allows valve 2| to close under force of spring 25, and it is thereafter held against its seat I8 by this spring plus the pressure of liquid refrigerant in tube i1 (Fig. l). The movement of piston 24 to the right is then stopped by the right hand plunger |88,A which is urged upward by spring |81 and engages notch |84 on its left side.

Pin |88in the piston 24' has meantime moved member |88 to the right, compressing spring. |80 between the shoulders on members |89 and |9i, the latter being pivoted at 200 at a point midway of the extreme positions of movement of pin |88. g5

This moves the upper end of member |8| to the left, so that it no longer bears against the right hand shoulder on part |82, but the movement is not enough to cause |8| to contact the left hand shoulder of part |92, hence valves |93 and |94 are not moved. Since the pressure against |83 tending to hold it closed is greater than the pressure acting upon |94 there is nothing to move either valve, but as a safety measure I prefer to employ a "snap-over device as indicated by ball |58, which engages one and then the Aother of the two cooperating notches in member|82 to guard against accidental movement by vibration.

The movement of piston 24' to the right has thus far been less than enough to contact the stem of valve 20, hence both liquid valves are still closed and the vapor valves left as at the start. I'he result is that liquid refrigerant in section 21 of the evaporator is still supplied to the section 28 through the expansion valve as before, until such time as the pressure upon the liquid falls to a point that allows it to evaporate in section 21 before going through the expansion valve. This will stop the refrigeration of section 28 and start the refrigeration of section 21, but the pressure in section 21 will remain appreciably higher than in section 28 because of the fad; that vapor cannot pass the restricted opening in the expansion valve as rapidly as liquid did (measured in weight of refrigerant). This causes a further drop of pressure in chamber |1| and allows bellows |12 to expand under the combined eifect of a lower surrounding pressure and a higher internal pressure. The rise of temperature is due to stoppage of refrigeration in evaporator section 28, which allows a greater degree of superheat in the refrigerant in chamber 1| than existed before during the refrigeration of section 28.

The expansion of bellows |12 pushes upward on 75 rocker |18, causing its point |91 to push downward on the right hand plunger |86, compressing spring |81 and releasing the piston to move farther to the right under the combined influence of pressure difference between the two ends of the piston 24 and the force of'spring |90 which was compressed in the previous movement and stopped just beyond its maximum compression in which it is urging `the piston to the right. This movement of the piston opens valve 20 by direct push and opens valve |93, simultaneously closing valve |94, by the contacto! `member |9I upon the left shoulder of |92.

This brings the valves into positions Vsimilar to those shown in Fig. 1 but there is little or no liquid refrigerant to spill into chamber |1| and thence into the suction line. Warm liquid refrigerant entering section 28 of the evaporator, which has been substantially evacuated and allowed to warm up somewhat, will rapidly melt free the ice that remains on the associated freezing surfaces in this section.

When the freezing of ice by evaporator section 21 has progressed to thepoint of again causing bellows |12 to contract, the left plunger |8|, which is now engaged in notch |85 and holding the piston at its extreme right position, will be withdrawn from this notch and thepiston will move tov the left under pressure of the liquid refrigerant which now acts upon its right hand end and the right hand plunger |86 will engage the right hand side of notch |84, holding the piston from farther movement until the liquid is substantially exhausted from section 28 and the bellows expands as before, to release the piston from completion of its travel, which in this case takes it back to the position shown in the drawing.

An adjustment for the lower bellows head |98 is provided by screw |99, by means of which the bellows may be positioned to give the spring |13 the required degree of compression or expansion to properly balance the contraction and expansion of the bellows so that the division of time between two adjacent portions oi.' the cycle will be satisfactory. By changing springs |82 and |81, or by providing adjustments for changing their working lengths independently, such 'as by providing adjustable stops for them at their lower extremities, it is possible to control the cycling of the system still further, prolonging or shortening the time of the piston at its two extreme positions by means of spring |82 and the time of the piston at its two intermediate positions by means of spring |81.

Fig. '1 shows an alternative construction of Fig. 6, with the toggle member I 65 substituted for ball |56 to hold the part |92' (corresponding to |92 of Fig. 6) in the position to which it has been moved by member |9l' (corresponding to |9| of Fig. 6). Part |65 is pivoted to the housing |10 at |69and when moved past its dead center position with relation to spring |61, retainer |68 and point |69 it snaps over to the opposite face of part |92. The result is that part |92' is held by spring |61 in its extreme right or extreme left position, to whichever of which it has been moved by part |9I'.

Part 19|' differs from part |9| of Fig. 6 in havingl no bearing on the pin 200, which is fixed to housing |10. Instead the part |9I' ts into hole in member |64 which is further shown in the perspective view, Fig. 8. Part |64 is pivoted on housing |10. This construction allows the spring |90 to be longer, giving it a more nearly constant strength through its working length and providing a greater angularity for the axis of the spring at each of its extreme movements, so that the push of the spring is more effective in moving piston 2l'.

Fig. 9 which is a fragmentary sectional view, shows parts of Fig. 6 to illustrate the use of an adjustment for springs |82 and |81, so that they may be independently adjusted. As illustrated in this figure, plunger |86 and spring |81 may be considered as representing either this pair of parts or as representing plunger |8| and spring |82. The compression of the spring is adjustable by means of the bushing III threaded into the housing |10. Access to bushing III is had by removing plug H2, which is provided with a gket to make a gas-tight joint with housing The references to ice making surfaces and water tanks in the foregoing description will be understood to refer to such devices as are disclosed` herein and in my co-pending applications. particularly Serial Number 697,124, led November 8, 1933, previously referredto.

Fig. 10 is a chart or graph` showing approximate temperature and pressure conditions affecting the bellows |12 of Fig. 6. Assuming that the bellows |12 is charged with the same fluid used as a refrigerant, in the system, containing some vapor and some liquid, and assuming that the suction chamber |1| is filled with refrigerant vapor at a constant saturated temperature condition, it will be seen that the fluid pressure acting externally upon the bellows will be exactly the same as that acting'internally upon it. This, however, is a condition which, if it exists at all. is maintained only momentarily in the cycling of the system as described.

There is actually a varying amount of superheat in the vapor surrounding bellows 12 and there is a certain time lag in the temperature within the bellows as compared with the temperature surrounding it, toward which latter temperature the fluid in the bellows is always being heated or cooled.

In Fig. l the upper curve indicates temperature variations in the suction passage during cycles as described in connection with Fig. 6, which suction temperatures are followed quite closely vby the temperature within chamber |1|. Starting with the valves in positions shown in Fig. 6 and as indicated by numbers at the top of the left hand (first ten minutes) portion of the graph in Fig. l0, we note that the suction temperature is rapidly dropping, due to refrigeration having been started by the opening of valve 20. This temperature curve is substantially that observed with methyl chloride as the refrigerant, operating at a suction pressure of about ve pounds, or of sulfur dioxide at a suction pressure of about eight inches of mercury below atmosphere.

With methyl chloride at five pounds suction pressure, under control of an expansion valve, the pressure surrounding the bellows will be practically constant during this part of the cycle. The temperature of the vapor around the bellows will gradually be reduced as the refrigerating process progresses, following a curve similar to the upper one above mentioned. Assuming now that the bellows is charged with sulfur dioxide, the bellows and its charge will be cooled by the methyl chloride vapor, resulting in the vapor pressure of sulfur dioxide in the bellows dropping somewhat as indicated by the curve marked "BO: bellows internal pressure. The vapor pressure within the bellows will thus be caused to drop to a pressure lower than that of the methyl chloride vapor surrounding it, whereas it started well above the ilve .pound suction pressure.

This cooling effect upon the bellows during the -flrst stage of operationl causes it to contract, actuating the mechanism as `described and re-y leasing the piston 24', thus causing valve 2| t close. suction pressure will' begin to drop as(- indicated by the curved marked -Cl-11C! suction pressure and at the same time the. temperature of vapor surrounding bellows |12 will rise. causing an increase of the sulphur dioxide vapor pressure within the bellows. 'Ihe two pressure curves recross and the excess of the external pressure action upon the bellows will soon cause it to contract and actuate the mechanism which opens valves and |83 and closes valve |84, thus initiating another cooling period. but refrigerating the other evaporator section.

The bellows is now affected in the same manner as at the beginning (left) of the chart in Fig. 10. The fresh supply oi' liquid methyl chloride brings the suction pressure back up to the five pound setting of the expansion valve, while the temperature of the vaporized methyl chloride surrounding the bellows drops, cooling the bellows so that its internal vapor pressure of sulphur dioxide drops. This causes the bellows to contract again and trip the mechanism which closes valve 20.

y With valve 28 closed the supply of liquid methyl chloride is stopped and the suction pressure drops while the suction temperature rises. This causes the bellows to expand, opening valves 2| and |94 and closing valve |83. Valve 20 remains closed, which brings us back to the start of the chart in Fig. l0.

Should the refrigerant in the system be sulphur dioxide, the same as the charge in the bellows, it will be noted that the pressure lines do not cross, hence for this combination of the same gas inside and out of the bellows it would be necessary to place a spring or weight so that it tends to compress the bellows. By assuming the spring |13 to be under tension instead of compression this condition is met.

For convenience in assembly it is desirable to have a rather low vapor pressure fluid in the bellows, as for instance ethyl chloride (Cal-IsCl). The curve of bellows internal pressure for ethyl chloride will be seen to cross thesuction pressure curve of sulphur dioxide.

Should it be desired to employ methyl chloride as the refrigerant and ethyl chloride yas the charge in the bellows, it will be seen from the chart that the pressure lines 'cross to only a slight degree at the end of the evacuating portion of the cycle` (when both liquid valves are closed). The use of this combination is, however, quite practicable when the spring |13 is used under compression to help the ethyl chloride expand the bellows.

Adjustments of the compression of spring |82 and of spring |81 independently, together with adjustment of spring |13 to vary its tension or compression, will accommodate the control to a wide variety of refrigerants and bellows charges. The design may be modified toA use a spring external of bellows |12, tending to compress it ii.' desired.y

The valves 36 and |24 (Figs. 1 and 3) may be Soon after this valve is closed the' varied in a number of ways, as shown byFigs. 11`

to 18, inclusive. These valves are ordinarily connected in parallel, either to act in the same direction, as in Fig. 3 or to act in opposite directions as in` Fig. l. While more than one valve is normally used in one of my ice-making systems, I show them singly for convenience and clarity of drawings. It will be understood that they are applicable to other types of refrigerating systems and that I include in this disclosure the planl of combining two or more of them in one housing or assembly as indicated and 3.

In all of these views solid arrows are used to indicate flow of highpressure refrigerant and dotted arrows are used to indicate flow of low by Fiss. 1. 2

pressure refrigerant. Either may be liquid or vapor, but in the case of Figs. 1l to 18, inclusive, the highv pressure refrigerant is always liquid.

Fig. l1 shows the c heck valve 2|! seated in body 2|8 under its own weight and the pressure oi' downwardly flowing liquidrefrigerant. An external thread 2|1, cut into the face of 2 I5, allows 4a limited fiow of refrigerant spirally' downward past the check valve 2|5 when in closed position so that low pressure refrigerantY discharges from the body 2|8 at the bottom. When high pres-'- sure liquid flows into the body 2| 8 at the bottom its pressure lifts the valve 2|5 so that liquid may flow freely past it. 'I'he taper employed is of sufficient included angle to preventv sticking of the valve in its tapered seat.

Fig. 12 shows avalve enclosed in the housing formed by members 2|8 and`2l8, which are separated by the dividing wall 220, on either side of which a suitable gasket is employed. Liquid refrigerant entering at the top through port 22| must flrst pass through the screen or filter 222 carried by valve 228 and then through passage 223 in the valve 228 to the capillary tube'which is sealed within the float 22|i,`its upper end connecting with passage 223 and its lower end allowing discharge of refrigerant at 226 into the interior of body member 2| 8 at reduced pressure. Thence the refrigerant flows out through port 221 to the evaporator. When flow is reversed and liquid refrigerant enters through port 221 it lifts the float 225 and unseats valve 228 fixed thereto to allow free flow of liquid without the necessity of passing through capillary 224 or screen 222.

Fig 13 is similar to Fig. l1 except that the housing 228 has a much smaller internal taper and the valve 230 is stopped by a definite seat 23| instead of by contact with side walls. The

spiral groove 232 formed in the outer wall of the valve member 238 allows a limited flow of refrigerant downward as before described when the valve is closed. Rei'rigerant passing downwardly through the groove 232 is discharged through passage 233 to outlet 234. Since seat 23| prevents a sticking contact in the tapered opening in the body, there will be some leakage of refrigerant longitudinally from thread to thread and this must be taken into account in designing .the thread. It is even possible to substitute annular grooves for the thread 232, using the labyrinth principle to obtain the desired restriction. Liquid flowing upwardly lifts the valve 230 from seat 23| and increases the clearance between parts 238 and 228 to allow relatively free flow of liquid upward. Lugs 235 on cover 238 stop the upward movement of valve 230 and prevent closing of port 231.

Fig. 14 shows downwardly owing refrigerant passing through a screen 222 fixed with respect to its housing and the capillary tube 224, as in Fig. 12, but upwardly flowing refrigerant unseats the check valve 238 instead of lifting the capillary tube assembly.

Fig. 15 shows a valve construction which acts on downwardly flowing refrigerant as an expansion valve, and on upwardly flowing refrigerant as a floating check valve such as that shown in Fig, 12. When liquid enters chamber 24| at the top it is stopped by valve 242 until such time as suction on outlet 243 reduces the pressure in chamber 244 of body 245 to a point that causes the sealed bellows 246 to expand under action of spring 241 and whatever atmosphere may be in it. This expansion causes the lower bellows head 248 to strike stop 249, after which the upper head 250 of bellowsv lifts and it in turn lifts valve 242 from its seat to allow a limitedflow of liquid refrigerant through port As soon as the pressure in the low side is thus increased to the desired point the bellows is compressed by such pressure and again hangs upon valve 242 to hold it closed. When liquid enters at the bottom through port 243 the bellows floats up against' stop 252 and holds the valve 242 open to allow free now of liquid upwardly.

Fig. 16 shows a valve construction which acts as a simple check valve in response to upward flow of liquid, but the valve 253, when seated against member 254 allows a limited flow of refrigerant through the tiny restricting passage 256. During upward flow of refrigerant the valve 253 opens to allow free flow of refrigerant and is limited in its movement in this direction by contact with the lower end of the fixed guiding post 255.

Fig. 17 is similar in showing another form of check valve 251 seating against part 258. Downward flow is restricted by the capillary passage 259 leading from the cross-drilled hole 260 to the bottom opening in 258.

Referring to Fig. 18, the valve will be seen to comprise a housing 20| containing a check valve member 202 and fitted with a gas-tight cover 203. The check valve member including the body 204, the gas-tight cover 205 and the capillary tube 208, is designed to be somewhat heavier than the liquid refrigerant employed in the system, in other words so that it will not float in the liquid refrigerant. The cover 205 has notches 206 to allow free flow of refrigerant and the cover 203 is provided with a stop to prevent the lower extremity of 204 from coming out of passage 2||. v

Liquid refrigerant entering through tube 2|2, as indicated by solid arrow, fills the interior of 20|, surrounding the valve member 202, enters the capillary tube at 209 and is discharged at reduced pressure through passage 2|0 into outlet 2||. The weight of the valve member 202 keeps the valve against its seat 2|4 and the pressure of liquid on an area equal to that of passage 2|| helps to hold the valve on its seat, butpassage 2|0 carries a limited flow of refrigerant past the seat.

When liquid refrigerant flows upward in passage 2|I it lifts the valve 2|3 from its seat 2|4 and flows out through tube 2|2 at substantially its initial pressure. As the interior of -housing 20| fills with liquid the assembly 202 is buoyed up and partially supported to further increase the opening of valve 2|3 and reduce the pressure drop.

The evaporator units or rings 3|, as indicated u in Figs. 1 and 3 by concentric circles, may be of types already disclosed in my co-pendlng application Serial Number 697,124 or may be of new types shown by Figures 19 to 26, inclusive, of the drawings herein.

Referring to Fig. 19 a. portion of the ice and water tank containing water 302 and including the ice-making surface 303, is shown in conical form, for freezing of ice rings or hollow cones 304, indicated by dotted lines. The bottom of tank 30| adjacent to cones 303 is formed with one or more concentric corrugations 305, which allow some flexibility between the cones 303 and the bottom of tank 30| to allow the individual cones in the tank to adjust themselves slightly to the conical evaporator units 306, o1' which a number are commonly associated with a single tank, having an equal number of icemaking surfaces or cones 303.

Further flexibility may be provided by mounting the evaporator units 306 in a flexible manner, preferably supporting them near their upper central portions as shown by the tube 301, which is attached to the inner wall 308 of evaporator unit 306. The conical wall 308 which is formed with a spiral groove in its outer surface is soldered or otherwise attached in a fluid-tight manner to the outer wall 309 of unit 306, forming the spiral passage 3|0 between these two parts.

The lower end of this spiral passage, which is designed to carry refrigerant, is connected with tube 3||. Tubes 301 and 3|| are attached in a fluid-tight manner at their lower extremi ties to the support 3|2, which is shown as being formed by an upper metal sheet 3|3 and a lower metal sheet 3|4. These sheets of metal are welded or otherwise joined together to form fluid-tight passages 3|5 and 3|6, which correspond to tubes or passages 30, 32 etc. of Fig. 1.

The dotted arrows in Fig. 19 indicate the preferred direction of flow of low pressure refrigerant through passage 3|6, tube 3| I, spiral passage 3| 0, supporting tube 301 and passage 3|5, in the order named. This direction of flow is reversed when high pressure (warm liquid) refrigerant is circulated for the purpose of melting ice rings 304 loose' from surface 303 to a1- low them to oat in water 302.

An alternative construction is shown by Fig. 20, in which the inner wall 308 of Fig. 19 is replaced by inner wall 3| 1, having vertical flutes or corrugations forming passages 3|8 in place of the spiral passage 3| 0 of Fig. 19. It will be understood that in Fig. 20 the tube 3|| is joined to the various passages 3|8 at their bottom ends and that tube 301 connects with the various passages 3|8 at their upper extremities, making an assembly very similar to that shown in Fig. 19, but with the low pressure refrigerant entering through tube 3|| to the lower ends of passages 3|8, from which it exits to tube 301 at the upper ends of passages 3|8.

These constructions are improvements over the types of sheet metal evaporator units shown in my application Serial Number 697,124 in that they provide greater strength to resist high internal pressures with light gauge metal sheets by having the inner sheets 30B and |31 stiffened by corrugation and by soldering or brazing them to outer sheet 309 along the corrugations or lines of contact intermediate of the top and bottom. They are also superior in regard to the provision for flexibility to allow better thermal contacts between ice freezing areas of the tank and the corresponding surfaces of the evaporator units.

Fig. 21 illustrates another modification of he evaporator unit construction in which the sheet metal walls 3|9 and 320 of the evaporator unit, somewhat similar to the one in Fig. 19, are formed integrally from sheets 32| and 322, which in turn correspond to sheets 3|4 and 3|3 of Fig. 19. Instead of employing the central tube 301, the tube 323 is arranged to conduct refrigerant vapor from the top of the spiral evaporator unit'to the passage 324, which corresponds to passage 3|5 of Fig. 19. Instead of the tube 3|| of Fig. 19 a passage 325 is formed between the two sheets of metal and joins passage 326, which corresponds to passage 3|6 of Fig. 19.

The insulating material 321, filling the space between sheets 323 and 329 of harder material, closes the opening at the bottom of the evaporator unit to prevent air circulation in and out of the inner space 330. This insulating material also protects the passages 3.24 and 326 from too rapid loss of heat to the surrounding air during the period when warm liquid refrigerant passes through them.

Fig. 21 also shows a modified form of control to actuate valve mechanisms such as disclosed herein and in my earlier application, above mentioned and identified. The bulb 33| charged with volatile iiuid 332 is connected by means of tube 333 to an expansible member such as a metal bellowsl or diaphragm-enclosed space and such expansible member is employed to actuate the.

valve or switch mechanism which controls the cycling of the evaporator unit. For example, when warm liquid in passage 3|0 has melted an ice ring free from surface 303 of Fig. 2i the temperature of bulb 33| and fluid 332 will rise, producing an increase of pressure in tube 33 and this pressure is employed to actuate a pressureresponsive'member for the purpose of initiating another freezing period on the surface from which ice has just been melted free.

One method of connecting the tube 333 for such operation would be, assuming that Fig. 21 represents one of the units 3| of the left hand evapor ator section in Fig. 3, to connect the tube 333 to tube N2 of Fig. 3 in place of connecting tube M2" to assembly |36". The vapor of fiuidl 332 (Fig. 21) will then replace the liquid, Mi in chamber |43 and will act to compress bellows |33, actuating rod |35 and lever |36 to start a freezing period in section 923 of the evaporator (Fig. 3). 'I'his Will occur in response to a rise of temperature at bulb 33| in one of the units 3| of section |23, and the result will be to start an ice-making period in the evaporator section :associated with the ice-making surfaces from which the ice rings have lately melted free.

Thus it will be seen that my invention is operable with cyclic ice-making periods initiated by the rise of temperature adjacent to surfaces from which ice has lately been melted free, as well as with ice-making periods initiated by the finishing of a freezing period by another evaporator section. This method may also be employed in systems including only one evaporator unit 3| or a single section of such units, all of which are refrigerated at one time.

An advantage of this method of employing the rise of temperature to initiate cyclic changes is that a greater temperature difference is available, providing a greater relative change of pressure than is obtained from temperature changes in the suction passage of the system. The temperature of bulb 33| will be about 33 F. during the freezing period, but will rise to 50 F. or thereabout after the ice has been melted free by the hot liquid refrigerant. The insulating material 321 confines the heat in space 330 when passage 3|0 is carrying warm liquid and it keeps heat out while passage 3|0 carries cold fluid. On this account the temperature of surroundingy air has little or no effect.

Bulb 33| may be connected rigidly for good thermal contact with conical part 320 oi the evaporator unit, or may be held in intimate contact with the inside of ice-making cone 303, as shown in Fig. 21, where the spring 334 is constantly urging bulb 33| upward and the tube 333 is free to move relative to part 320. It is advisable to employ one method or the other to insure uniformity of control, but either will operate satisfactorily.

In Fig. 22 the ice-water tank 30| is provided with a downwardly projecting inverted cone or cup-shaped ice-making member 335, on the inner surface of which ice is frozen, as indicated by 336. The tank 30| contains Water 302 as before. Refrigeration and heating effects are applied by fluid passing through the coil 331 of tubing which is D formation in section and arranged so that the fiat side fits with good -thermal contact against the outer wall of cup 335. Connections 338 and 339 lead from the two ends of this coil to refrigerant connections as before described.

The coil 331 is suported in a semi-rigid and somewhat resilient manner by the mat 340 of insulating material which is retained and supported by flat sheets 34| and 34|. 'I'he coil, being somewhat flexible and not rigidly supported, will adapt itself to the form of cup 335 and provide good thermal contact therewith. The weight of tank 30| and its contents is carried through the areas of contact between ice-making areas of the tank wall and the evaporator units as is the preferred practice in all of these constructions, hence the weight of the tank and its contents assists in maintaining the intimate thermal relation of ice-making areas and evaporator units, the latter being coil 331 in the case of Fig. 22.

The bulb 3132, contacting the bottom of cup 335 in Fig. 22 serves the same purpose as bulb 33| in Fig. 2l, it being supported like the evaporator coil 337 in a semi-rigid manner so that the thermal contact with cup 335 is maintained. This bulb, which is preferably made of two metal stampings soldered, brazed or otherwise secured together in a fluid-tight manner as in the case of bulb 33|, is further illustrated in Fig. 23, which is a sectional view taken on the line 23-23 of Fig. 22.

As seen in Fig. 23, this bulb is provided with a charge of fluid 332, as is bulb 33| of Fig. 2l. To insure a closer thermal relation between this fluid, 'particularly that portion of it which is in the liquid phase, and the upper wall of bulb 342, which is in contact with cup 335, ns383 are pro vided on the upper wall of the bulb interiorly thereof and project downwardly into the liquid within the bulb. 'I'he tube 345 connects bulb 342 to pressure responsive means in the same manner as described in connection with tube333 of Fig.21, hence the same features of control are provided.

Fig. 24 shows another type of evaporator element 3| in which the element is formed by the same two sheets of metal which are employed tu enclose the passages 324 and 326, as in Fig. 21.

The evaporating space 345lbetween these two sheets is here shown as a plain annular space of conical section in a plane with its axis, but it may be a spiral passage as in Fig. 2l, or formed with vertical corrugations as in Fig. 20. This con-- struction differs from that shown by Fig. 21 in having the passage 346 formed by welding or soldering a third sheet of metal 341 to sheet 32| in such manner as to form a passage between ports 348 and 349, both of which perforate sheet 32|. Port 348 connects evaporator space 345 with passage 346 and port 349 connects passages 346 and 324. The sheet 341 is attached to sheet 32| in the manner illustrated in Fig. 25.

Fig. 26 shows another form of the spirally wound D sectioned tube evaporator unit, with the coil inside of the ice-making cup instead of outside of it as in Fig. 22. 'I'he tank 30| and water 302 are similar to these items in other views, but the conical ice-making surface 350 has a steeper angle and terminates .at the top with a substantially straight-sided extension 352 formed integrally with it. This form of cone makes cones of ice 35| which will nest together as shown in Fig. 27, while the extension 352 insures against the formation of ice over the top of the cone in the tank bottom. When ice is formed over the top of a cone to make an inverted cup of ice, I have found that the ice does not free itself from the surface upon which it has been frozen as readily as is usual in the case of a ring of ice.

The tube 353, which connects with the refrigerant manifold as before described, leads directly into the spiral coil 354 of D sectioned tubing, thence to the tube 355, which also connects with a manifold. Since the total length of the tube is quite short, it can be coiled around a form, through which the end 355 extends, from the top downward, ending with the portion 353. The coiled tube, while still on the form, is then pressed into a female tank cone 350 to form the coiled portion into the D section and make it fit the tank cone 350 more exactly. The end 355 is bent to shape after removing the spiral tube from the form by unscrewing it therefrom. Clips 356 secure the finished coil to a suitable support 351, allowing enough flexibility in the tubing to let the fiat outer walls of the D section part of the coil fit snugly against the inner wall of the cone 350.

Referring to Fig. 28 it will be understood that vaporized refrigerant passing through the tubes 1I is compressed by the compressor 12, condensed in the condenser 13 and collected as liquid in the receiver '14, from which the liquid refrigerant passes through the tube 15 which enters the refrigerated space enclosed within the insulated wall 402. After passing through this insulated wall the tube 15 is enclosed by thermal insulation as indicated by broken line 403.

Liquid refrigerant is conducted by the tube 15 to the coils 404 and 405 surrounding the bellows chambers 406 and 401, respectively, and then through tubes 408 and 409 to the interior of liquid valve housings 4I0 and 4Il. The liquid refrigerant is stopped in housing 4H by the valve 4|3 which is shown closed in this view, while the corresponding valve 4|2 on the right hand side is open, allowing liquid refrigerant to pass through the passages formed by the flutes in the stem of the valve 4|2 into the chamber 4|6 and tube 4I8 leading to the interior of valve housing 420. Since the valve 422 is closed the liquid refrigerant cannot flow in that direction but flows through tube 424 to the manifold 425 which is better shown in Fig. 29. From manifold 426 the liquid flows through the several tubes 428 to the right hand group of evaporating units 3| which are connected in parallel between the manifold 426 and the manifold 430. After passing through the various evaporator units 3| the liquid flows through the manifold 430 (see Fig. 29) to the capillary restricting device 40|, which causes a reduction of pressure such that the'refrigerant will evaporate in the left hand group of evaporator units 3| after passing through the manifold 425 (see Fig. 29). The refrigerant chamber within each of the evaporator units 3| is shown as the conical, annular space 432 in Fig. 28.

The vaporized refrigerant then passes through tubes 421 (see Fig. 29) to the manifold 425 and out through the tube 423 to the interior of valve housing 4|9. It is at this point free to pass through the tube 4|1 and into the chamber 4|5 where it is stopped on one side by the diaphragm 435 and on the other side by the closed valve 4| 3. Valve 42| in housing 4| 9 is, however, open. allowing the refrigerant vapor to flow along the iiuted stem of the valve 42| into the chamber 431 and out the passage 438 to the suction tube 1|, thus completing the circuit.

During the portion of the cycle thus represented and described, the warm liquid refrigerant passing through the right hand group of the evaporator units 3| will supply heat for melting the cones of ice 440 free from the conical surfaces 442 so they may float upwardly in the water contained within the tank 444. At the same time the low pressure refrigerant in spaces 432 of the left hand group of evaporator units 3| will be causing the freezing of similar cones of ice 44| on the surfaces 443. Before the cones of ice 440 have melted free from the surfaces 442 they have close thermal relation therewith and the heat of the warm liquid refrigerant passing through the right hand spaces 432 is mainly utilized in melting the ice free from the surfaces 442. As soon as the ice 440 has detached itself from the surfaces 442 and floated upward in the Water contained in the tank 444 the rate of heat transfer from the warm refrigerant in right hand spaces 432 to the surfaces 442 will be materially reduced and therefore the outer wall of the evaporator units 3| will rise in temperature and by conductivity will warm its upper extension 446 and thereby the bulb 440 which is socketed therein in good thermal contact therewith. In this respect it is to be understood that the rate of transfer of heat between a metal wall and ice is greater than between the same wall and water of the same temperature as the ice. This causes the volatile liquid 450 contained in the bulb 448 to vaporize until its vapor pressure balances with the increased temperature and this vapor pressure acting through the tube 452 causes the bellows 454 to expand moving the push rod 456 to the left and thereby moving the lever 451 which is pivoted upon the shaft 462. This move ment is opposed by the toggle spring 463 and assisted by the valve spring 465 acting upon the left hand vapor valve 42|.

This counter-clockwise movement of the lever 451 is carried by the expansion of the bellows 454 until the arcuate portion 458 of lever 451 disengages the connecting rod 466, whereupon the diaphragm 436 is moved to the left by the high pressure of liquid refrigerant within chamber 4|6 while the shoulder of connecting rod 466 disengaged by arcuate portion 458 of lever 451 acts upon the cam surface 460 of lever 451 to cause the lever to move further in a counter-clockwise direction until the spring 463, snapping over center, re-expands to produce a still further movement in a counter-clockwise direction and l (i l semi-rigid manner as above the plate 415.

the lower end of lever .451 engages the stem of vapor valve 422. The right hand vapor valve 422 is thus moved from its seat by the combined effect of spring 463 and the movement of diaphragm 436, which also causes diaphragm 435 to move to the left, striking the stem of valve 4|3 and causing this valve to open. The connecting rod 466 having moved to its extreme left position, the arcuate portion 459 of lever 451 drops into the notch in the connecting rod 466 and holds the connecting rod 466 at its extreme leftward position. At the same time the valves 4|2 and 42| are closed by their respective springs while valves 4|3 and 422 are opened. The upper end of lever 451 is free t9 move to its extreme leftward position because of the fact that the bellows 453 is contracted due to the low temperature existing within the bulb 441.

The pivot shaft 462 is secured to the casing 439 as shown in Fig. 31. Any suitable mechanical connection may be made between the lever 451 and the connecting rod 466, such for instance as a toggle linkage which would serve to hold the connecting rod 466 at either of its extreme movements as is done with the piston 24 in Fig. 1. A bellows may be substituted for the diaphragm 436 and another bellows for the diaphragm 435 as suggested in other views of the drawings. The expansive movement of such a bellows or diaphragm, having a much larger area than the valves 42| and 422 and being acted upon by the same liquid pressure, will supply ample energy for opening the valves against liquid pressure and their respective springs.

After the counter-clockwise movement of lever 451 as above described, the path of refrigerant from the tube 15 will be through the coil 405, the tube 409, past the open valve 4|3, through the tube 4|1 and the tube 423 to the manifold 425 which distributes it to the left hand evaporator units 3| for the purpose of melting free the rings of ice 44| while new rings or cones of ice are frozen to replace the recently released cones of ice 440, which are now floating in the water in tank 444. The heat supplied by the warm liquid refrigerant to the left hand evaporator units 3l will melt the cones of ice 44| free so that they likewise float away and the heat will then cause a rise of temperature at the bulb 441 which will in turn cause the bellows 453 to expand pushing the rod 455 against the lever 451, causing it to move in a clockwise direction under forces similar to those which moved it to the left as above described. This will bring the valve mechanism back to the position shown in Fig. 28. The point 461, which supports one end of the spring 463 is attached to the lever 451 and moves with it as indicated in Fig. 3l, while the point 460 is stationary.

The evaporator assembly is supported in a The insulating material 416 supports the evaporator units 3| but is preferably made of material liaving sufficient compressibility to allow these evaporator units to adapt themselves to fit the interior of thecones 442 and 443 which are integral with the removable tank 444. -The bulbs 441 and 448 are supported by the split tubular inserts 411 which are seen in horizontal cross section in 30. Since the tubes 45| and 452 are of small diameter and quite flexible, they may be readily straightened out so that the sheet 415 can be removed from the insulation 416, whereupon thq bulbs 441 and 448 together with their respective split bushings 411 may be withdrawn from the balance of the assembly. By providing openings in the sheets 415 large enough to allow the passage of the bulbs 441 and 440 the entire evaporator assembly may be separated from the valve assembly by removing these bulbs and by disconnecting suitable unions (not shown) in the tubes 423 and 424.

While the liquid valve 4|2 is open the supply of warm liquid refrigerant will be flowing through the coils 404 to increase the temperature of the bellows 454. This is for the purpose of preventing condensation of the volatile `fluid 450 from the bulb 448 into the bellows 454. This heating of the bellows 454, although to a higher temperature than is ever attained by the bulb 448, will not cause the bellows to expand since the bulb 448 has ample volume to contain all of the fluid in liquid form.

It will be noted that the insulating material indicated by the broken line 403 surrounds all of the valves and passages which are called upon during any portion of the cycle to convey warm liquid refrigerant within the refrigerated space enclosed by the insulated wall 402. This is for the purpose of conserving the heat in the liquid refrigerant until it can be employed for the purpose of melting the cones of ice free from the surfaces 442 and 443. Instead of providing a heat exchanger between the cold vapor line and the warm liquid line, I purposely hold the heat in the liquid and employ it to free the cones of ice from they surfaces upon which they have been frozen.

It will also be noted that in Fig. 28 in particular, all surfaces that are liable to be refrigerated to a temperature of less than 32 degrees F. are insulated, not only to prevent the loss of heat from such of them as may also contain'warm liquid refrigerant during certain portions of the cycle, but also to prevent the air in the cabinet in which the mechanism is housed from becoming dehydrated from contact with and causing frosting of a surface or surfaces below 32 F. in temperature. This preferably applies to evaporating surfaces, connecting tubes, and the valve mechanisms in all the appropriate figures of the drawings, and where, as illustrated in Fig. 1, a separate evaporator is provided for the purpose described, it also is preferably provided with an insulating covering as indicated to fully realize this advantage. It will be understood in this connection that itis not necessary for the water tank 444 to be insulated except at those areas immediately surrounding the evaporator elements 3|, as the remaining walls of the tankwill never be below freezing temperature and consequently they may be employed for direct contact with the air in the enclosed cabinet for cooling such air and thus realize the usual purpose of a mechanically refrigerated cabinet Without encouraging more than a minimum amount of condensation of the moisture in the air upon the tank walls.

Although a number of different modifications of the salient features of the present invention are disclosed in the accompanying drawings, it will be readily seen by those skilled in the art, upon the disclosure to them of the teachings herein, how the structures disclosed may be modified and/or changed without affecting the principles of the broad invention. Accordingly, it is to be understood that formal changes may be made in the specific embodiments of the invention disclosed without departing from the spirit and substance of the broad invention, the scope of whichl is commensurate with the appended claims.

What is claimed is:

1. A refrigerating system, an automatically cycling ice maker incorporated in said system, and a yieldable member exposed to the effects of `refrigerant in a suction passage of said system an evaporator for refrlgerating a wall area of said tank and positioned in thermal contact therewith,

.a thermally responsive device, means 'controlled by said thermally responsive device for controlling the operation of said evaporator in a manner to insure freeing of ice from the inner surface of said tank when such surface is not refrigerated, and means resiliently urging said device into contact with said wall area.

3. In an ice making apparatus having a cyclically operating refrigerating system, a water tank having a submerged wall area, an evaporator for refrigerating said area positioned in thermal contact therewith, a thermally responsive device, means controlled by said thermally responsive device for controlling the operation of said evaporator independently of the starting and stopping of said system, and yieldable means supporting said device in spaced relation to said evaporator and in thermal relation to said area.

4. In an ice maker of the type disclosed herein, designed to harvest ice automatically by flotation. a plurality of evaporator units and a thermally affected element in thermally adjacent relation to one of said units and connected to control means for effecting cyclic operation of said ice maker.

5. In an automatic ice maker of the type described, a thermostat controlling the cycling thereof, a water tank, an evaporator section contacting an area of a wall of said tank, and a temperature responsive element of said thermostat contacting a portion of the wall of said tank on its cuter surface proximate to the area contacted by said evaporator section.

6. In an automatic ice maker, a tank for water and ice, a heating and cooling element associated with a wall of said tank to form ice thereon and release ice therefrom, means for alternately heating and cooling said element, and thermostatic means for controlling the first mentioned means so constructed and associated with said element as to initiate a cooling cycle of the f'lrst mentioned means upon a predetermined rise in temperature of said element occasioned by the release of ice from said surface.

7. In a refrigerating system including a refrigerant circulating system, means forming a vapor passage connected therewith, control means assoelated with said vapor passage so constructed and arranged as to be responsive to vapor pressure changes and to temperature changes in said passage and to move in opposite directions, one in response to a fall of temperature and the other in response to a fall of pressure in the same passage. i

8. In a refrigerating system, a plurality of control means for saldsystem, common actuating means for said control means including a flexible wall member exposed on one side to refrigerant in said system, said member being so constructed and arranged as to be caused to move alternately in opposite directions by changes in the condition of the superheat of said refrigerant and thereby to actuate said control means.

9. In an automatic ice maker including a water tank and means for alternately forming ice on and releasing ice from a surface thereof including a refrlgerating system, a high pressure side of said system, a low pressure side of said system, means forming a refrigerant passage connecting said sides, and means for obtaining mechanical energy from refrigerant circulating through said passage for performing an automatic function of said ice maker.

10. In a refrigerating system, an ice maker operated by said system, means forming a refrigerant passage having a liquid refrigerant in a portion thereof, a valve controlling the flow of said liquid refrigerant, a chamber of variable effective volume into which liquid refrigerant may pass when said valve is open, the valve being held open by the contraction of the effective volume of said chamber and allowed to close when the effective volume of said chamber expands, and cyclically operated means for allowing the effective volume of said chamber to expand under the pressure of said liquid refrigerant.

1l. In a refrigerating system having a refrigerant therein and having a high pressure and a low pressure side, a valve diverting refrigerant flow in said system, and means actuated by the refrigerant pressure of said high pressure side for moving said valve independently of fluid pressure effects upon the valve itself.

12. In a cyclically operating refrigerating system, control means comprising a pair of opposed fluid-actuated parts, a movable part arranged to be moved in opposite directions by said fluid actuated parts, a stop for said movable part, thermally responsive means for periodically actuating said stop to release said movable part to allow movement thereof, and means actuated by said movable part to periodically effect the cyclic operation of said system.

13. In a cyclically operating refrigerating system, a member movable in opposite directions, a stop for locking said member against movement, thermally responsive means for operating said stop, means alternately acting in opposite directions to move said member, and means actuated upon movement of said member to periodically effect the cyclic operation of said system.

14. In a cyclically operating refrigerating system, a movable member, means for subjecting said member to the influence of pressure changes in said system to alternately move it in opposite directions, a stop for locking said member against said movement, thermally responsive means for operating said stop, and means actuated upon movement of said member to periodically effect the cyclic operation of said system.

15. In a refrigerating system, a valve mechanism for effecting cyclic operation of said system, a plurality of flexible-walled members with their flexible walls exposed on one side to varying refrigerant pressures within the circulatory path in said system, the said valve mechanism being controlled by thermally produced expansions and contractions of said flexible-walled members, and means preventing said flexible Walled members from actuating said valve mechanism improperly in response to other temperature and pressure variations in said system.

16. A refrigerating system employing a refrigerant which is condensed under pressure in a high pressure zone of said system and evaporated in a low pressure zone of said system, a member acted upon by pressure of said high pressure zone, a toggle mechanism holding said member from moving under the said high pressure. and means for releasing said toggle mechanism so that said high4 pressure will move said member for the purpose of producing a cyclic change in the operation of said system.

17. vIn a refrigerating system, an automatic ice maker, three or more evaporator sections in said ice maker, and cycling means including means responsive to variations in temperature of said system so-constructed and arranged-as to cause said sections to be refrigerated for the making of ice in regular progression and so that each section is refrigerated for less than half of the operating time of said system while a longer period in each cycle is 'allowed for melting ice free from the surfaces upon which it is frozen.

18. In an ice maker of the type described, a plurality of evaporator sections and ice making surfaces associated therewith, and means responsive to variations in temperature in said system so constructed and arranged as to effect cyclic operation of said system to employ one of said sections for freezing ice while two or more other said sections are warming up to allow ice previously frozen thereby to melt free from the surfaces upon which it was frozen.

19. In an ice maker including a refrigerating system, a plurality of evaporator' sections in said system and ice making surfaces associated therewith, and liquid refrigerant pressure actuated means so constructed and arranged as to effect cyclic operation of said sections whereby one of said sections is operated to freeze ice while two or more other sections are warming up to allow ice previously frozen by such other sections to melt free from the surfaces upon which it was being designed to allow free ow of liquid refri'gerant into said passage and to restrict the iiow of refrigerant in the opposite direction, an evaporator associated with each of said devices, means for supplying liquid refrigerant to said passage by passing it first through one of said evaporators which is thereby heated by the liquid refrigerant, and means for removing vaporized refrigerant from another of said evaporators while liquid refrigerant is supplied to said last vmentioned evaporator from said passage through one of said pressure reducing devices, land automatic cyclic means for shifting the flow of refrigerant to heat the last mentioned evaporator while the first mentioned evaporator is refrigerated.

21. In a refrigerating system, an evaporator section arranged to be alternatelyv cooled by* evaporation and warmed by high pressure liquid refrigerant, a second evaporator section which is being cooled by evaporation of refrigerant supplied through the first mentionedv evaporator section while said first mentioned section is being supplied with warm liquid refrigerant and cyclic means for stopping said supply of warm liquid refrigerant until saidliquid refrigerant ceases to pass to said second section.

22. In a refrigerating system, a check valve in a refrigerant passage of said system, a seat for said check valve, a float located in said refrigerant passage on the side of said seat opposite said valve and operably connected with said valve, a

capillary flow restricting device arranged to pass a limited flow of refrigerant through the said valve when it is closed, and means actuated by saidviioat for lifting the said valve from its seat when liquid refrigerant is admitted to said passage from the' opposite direction so as to lift the float.

23. In a refrigerating system. a check valve in a refrigerant passage of said system, and a capillary passage connected in parallel with said check valve so that a restricted flow of refrigerant is provided in the direction of flow which causes the said check valve to close, and means acting in response to a changing temperature condition for causing a reversal of refrigerant flow through said check valve.

24. In a refrigerating system, a check valve in a refrigerant passage of said system, a seat for said check valve, and a helical groove vin one of the lmating surfaces of said valve and seat to pass a limited flow of refrigerant when the check4 valve is closed.

25. In a refrigerating system, a refrigerant circuit, a passage in said circuit, a check valve closing said passagein one direction, a capillary passage allowing restricted fiow of refrigerant in this direction when the valve is closed, and oat means to assist in holding said check `va1ve open when the flow of refrigerant is reversed.

26. In an automatic ice maker of the type described, a water and ice tank having a plurality of conical surfaces and a plurality of conical evaporator sections for mating engagement with said surfaces and so constructed and flexibly supported that the various said sections will adJust themselves to said mating conical surfaces of the water and ice tank.

27. In an ice making system, a tank containing water, an ice making section in a wall of said tank, a coil of tubing contacting said sec- `tion on the side opposite from the water contained in said tank and having the said tubing flattened on its side next to said wall section, the said tubing being flexible to an extent which allows it to contact the said wall section intimately, the tank being removable from said coli, and a refrigerating system so constructed and arranged as to periodically refrigerate said coil to freeze ice on said section in said tank and then stop such refrigeration and allow said ice to melt free from said section.

28. In an ice making apparatus, a tank for ice and water, a frusto-conic ice making surface forming a part of a wall of said tank, and joining said wall at the larger diameter of said surface, and a non-refrigerated extension joining the smaller end of said surface concentrically therewith and having its surface angularly disposed with respect to said conic surface.

29. In a. refrigerating system, an evaporating unit comprising a conic wall and a second wall of corrugated section contacting the rst mentioned wall in its inner surface and sealed thereto to form a tortuous evaporating space therebetween.

30. In a refrigerating system, an evaporating unit comprising a sheet of metal in conic form and a second sheet of metal sealed., thereto to form a helical passage for refrigerant between said two sheets of metal.

31. In a refrigerating system, an evaporating unit comprising two conical sheet metal parts, one within the other and the two joined together to enclose an evaporating chamber, the said two sheets being attached together at points intermediate of the axial length of said evaporating chamber. 

